JP6104620B2 - Rolling bearing - Google Patents

Rolling bearing Download PDF

Info

Publication number
JP6104620B2
JP6104620B2 JP2013016340A JP2013016340A JP6104620B2 JP 6104620 B2 JP6104620 B2 JP 6104620B2 JP 2013016340 A JP2013016340 A JP 2013016340A JP 2013016340 A JP2013016340 A JP 2013016340A JP 6104620 B2 JP6104620 B2 JP 6104620B2
Authority
JP
Japan
Prior art keywords
seal
core material
outer ring
base end
end portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2013016340A
Other languages
Japanese (ja)
Other versions
JP2014148992A (en
Inventor
毅 香田
毅 香田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp filed Critical NTN Corp
Priority to JP2013016340A priority Critical patent/JP6104620B2/en
Publication of JP2014148992A publication Critical patent/JP2014148992A/en
Application granted granted Critical
Publication of JP6104620B2 publication Critical patent/JP6104620B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Description

この発明は、例えば、高速回転が要求される自動車に使用される外輪回転で用いられるシール付の転がり軸受に関する。   The present invention relates to a rolling bearing with a seal used in outer ring rotation used in, for example, an automobile requiring high-speed rotation.

従来の外輪回転用軸受は、空間容積を増やしてグリース封入量を増やすことで寿命向上を図っていた。しかしその結果、シールの外径が大きくなり、グリースの内部からの圧力を多く受けてしまっている。したがって、シール外径部からのグリース漏れに対し、耐力が低下している。
グリース封入量が多いことはグリース寿命が長くなるが、グリースが漏れてしまえば逆に短寿命となる。また、グリース量が多いとグリース攪拌抵抗も大きく、初期温度上昇が高くなるため、シールゴム材の劣化を早めることになる。 Conventional outer ring rotating bearings have been designed to improve the service life by increasing the volume of grease by increasing the space volume. However, as a result, the outer diameter of the seal is increased, and a large amount of pressure is received from the inside of the grease. Therefore, the proof stress is reduced against grease leakage from the seal outer diameter portion.
If the amount of grease is large, the grease life will be longer, but if the grease leaks, the life will be shorter. In addition, when the amount of grease is large, the grease stirring resistance is large and the initial temperature rise is high, so that the deterioration of the seal rubber material is accelerated.

従来の技術では、熱劣化に強いゴム材質や、発熱の小さいグリースを選定するなどしてグリースを漏れ難くする対策をしている。また、軸受の外輪内径寸法を小さくし、グリースの内部からの圧力を低下させることで、グリース漏れを防止している（特許文献１）。   In the conventional technology, measures are taken to make it difficult for the grease to leak by selecting a rubber material that is resistant to thermal degradation or a grease that generates little heat. Further, grease leakage is prevented by reducing the inner diameter of the outer ring of the bearing and reducing the pressure from the inside of the grease (Patent Document 1).

特開２０１２−０７２８１３号公報JP 2012-072813 A

図１１（Ａ）に示すように、従来の軸受を高温・高速条件で外輪回転させた場合、シール５０が劣化し易いことに加え、グリースＧｒに大きな遠心力が付加されるため、軸受空間内の圧力が上昇する。この圧力の上昇により、外輪５１に対してシール５０が相対的に移動することで、図１１（Ｂ）に示すように、シール５０と外輪５１との間に隙間ができる。最終的に、図１１（Ｃ）に示すように、外輪５１とシール５０の嵌合部からグリース漏れを発生させる事象が起きている。この対策方法としてシール嵌合力を強化することでグリース漏れ防止の効果が確認できているが、シール嵌合力を強化するためには、シール締め代を増加させる必要があり、組立性つまりシール挿入性が悪化する問題がある。   As shown in FIG. 11A, when the conventional bearing is rotated at the outer ring under high temperature and high speed conditions, the seal 50 is liable to deteriorate and a large centrifugal force is added to the grease Gr. The pressure increases. Due to this increase in pressure, the seal 50 moves relative to the outer ring 51, thereby creating a gap between the seal 50 and the outer ring 51 as shown in FIG. Finally, as shown in FIG. 11C, an event that causes grease leakage from the fitting portion between the outer ring 51 and the seal 50 occurs. As a countermeasure against this, the effect of preventing grease leakage has been confirmed by strengthening the seal fitting force, but in order to strengthen the seal fitting force, it is necessary to increase the seal tightening margin. There is a problem that gets worse.

シールの嵌合力を向上するためには、シール締め代を増加させ、芯金外径を大きくする必要があるが、背反としてシール挿入性が低下する。以下に事例を示す。
図１２（Ａ）は、従来例のシール等の断面図であり、同図（Ｂ）は、図１２（Ａ）の要部の拡大図である。図１２（Ａ）に示すように、芯金外径Ａ１を大きくしてシール５２の嵌合力を向上させると、図１２（Ｂ）に示すように、外輪シール溝５３における溝底５３ａとシール５２との間に、すきまδ１ができる。このすきまδ１ができる理由は、芯金と外輪シール溝口間に余裕がなく、溝底５３ａ以外の部分に肉を逃がしてしまうものと考えられる。 In order to improve the fitting force of the seal, it is necessary to increase the seal tightening margin and increase the outer diameter of the cored bar. Examples are shown below.
12A is a cross-sectional view of a conventional example of a seal and the like, and FIG. 12B is an enlarged view of a main part of FIG. As shown in FIG. 12A, when the outer diameter A1 of the metal core is increased to improve the fitting force of the seal 52, the groove bottom 53a and the seal 52 in the outer ring seal groove 53 are obtained as shown in FIG. A gap δ1 is formed between The reason why this clearance δ1 can be formed is that there is no allowance between the metal core and the outer ring seal groove and the meat is allowed to escape to a portion other than the groove bottom 53a.

この発明の目的は、外輪回転で用いられる転がり軸受において、組立性の向上を図ると共に、シール嵌合力の向上を図り、グリース漏れを抑制することができる転がり軸受を提供することである。   SUMMARY OF THE INVENTION An object of the present invention is to provide a rolling bearing that can improve assemblability, improve a seal fitting force, and suppress grease leakage in a rolling bearing used in outer ring rotation.

この発明の転がり軸受は、内外輪間の軸受空間を密封するシールを有し、このシールの外径側の基端部が外輪シール溝に嵌合され外輪回転で用いられる転がり軸受において、前記シールは、環状の芯材とこの芯材を覆う弾性部材とを有し、前記芯材は、少なくとも前記基端部が弾性的に縮径可能な部位であり、前記シールは、前記基端部を前記外輪シール溝に嵌合するとき、前記基端部を半径方向内方に弾性変形させても、前記基端部が前記外輪シール溝に嵌合した状態で弾性復帰する前記基端部を備え、前記芯材の外径部は、前記外輪シール溝の入口径よりも小さく、前記芯材の外径部に、この芯材の外径縁部分が残るように円周方向に沿って複数の孔または切欠きを備え、前記複数の孔または切欠きを備えることにより、前記芯材の前記外径縁部分を弾性的に縮径可能としたことを特徴とする。 The rolling bearing according to the present invention has a seal that seals a bearing space between the inner and outer rings, and the base end portion on the outer diameter side of the seal is fitted in the outer ring seal groove, and the seal is used in the rotation of the outer ring. Has an annular core material and an elastic member covering the core material, wherein the core material is a portion where at least the base end portion can be elastically reduced in diameter , and the seal includes the base end portion. wherein when fitted to the outer ring seal groove, even if the elastic deforming said proximal end portion radially inwardly, you elastic return in a state where the base end portion is fitted in the outer ring seal groove said proximal portion The outer diameter portion of the core material is smaller than the inlet diameter of the outer ring seal groove, and the outer diameter edge portion of the core material remains in the outer diameter portion of the core material along the circumferential direction. By providing a plurality of holes or notches, and by providing the plurality of holes or notches, The diameter edge portion, characterized that you have a resiliently contracted.

この構成によると、シールの外径側の基端部を外輪シール溝に嵌合するとき、基端部を半径方向内方に弾性変形させて縮径させる。このシールの基端部が外輪シール溝に嵌合した状態で、シールの基端部が弾性復帰する。このように芯材を、少なくとも前記基端部が弾性的に縮径可能な部位にしたため、シールの基端部を外輪シール溝へ挿入するとき、シールの基端部が半径方向内方に弾性変形したまま外輪シール溝に嵌り込み易くなり、転がり軸受の組立性の向上を図ることができる。またシールの基端部が外輪シール溝に嵌合した状態で基端部が弾性復帰するため、シール嵌合力の向上を図り、軸受からのグリース漏れを抑制することができる。   According to this configuration, when the base end portion on the outer diameter side of the seal is fitted into the outer ring seal groove, the base end portion is elastically deformed radially inward to reduce the diameter. With the base end of the seal fitted in the outer ring seal groove, the base end of the seal is elastically restored. As described above, since the core material is at least a portion where the base end portion can be elastically reduced in diameter, when the base end portion of the seal is inserted into the outer ring seal groove, the base end portion of the seal is elastic inward in the radial direction. It becomes easy to fit into the outer ring seal groove while being deformed, and the assemblability of the rolling bearing can be improved. Further, since the base end portion is elastically restored in a state where the base end portion of the seal is fitted in the outer ring seal groove, it is possible to improve the seal fitting force and suppress grease leakage from the bearing.

前記芯材の外径部に、この芯材の外径縁部分が残るように円周方向に沿って複数の孔または切欠きを備え、前記複数の孔または切欠きを備えることにより、前記芯材の前記外径縁部分を弾性的に縮径可能とした。この場合、一般的に用いられる芯材に、例えば、打ち抜き加工を施すことで、前記外径縁部分を簡単に設けることができる。したがって製造コストの低減を図れる。 By providing a plurality of holes or notches along the circumferential direction so that an outer diameter edge portion of the core material remains in the outer diameter portion of the core material, and by providing the plurality of holes or notches , the core The outer diameter edge portion of the material can be elastically reduced in diameter . In this case, the outer diameter edge portion can be easily provided by, for example, punching a commonly used core material. Therefore, the manufacturing cost can be reduced.

参考提案例として、前記芯材の前記外径縁部分を、前記芯材における外径部の残余の部分よりも拡径させたものとしても良い。この場合、シールの基端部を外輪シール溝に嵌合するとき、前記外径縁部分が半径方向内方に弾性変形することで、シールを外輪シール溝に容易に挿入し得る。シールの基端部が外輪シール溝に嵌合した状態で、前記外径縁部分が弾性復帰することで、シール嵌合力の向上を図れる。 For reference Proposed Example, the outer diameter edge portion of the front Kishinzai may be those obtained by diameter than the remaining portion of the outer diameter portion of the core material. In this case, when the base end portion of the seal is fitted into the outer ring seal groove, the outer diameter edge portion is elastically deformed radially inward, so that the seal can be easily inserted into the outer ring seal groove. In the state where the base end portion of the seal is fitted in the outer ring seal groove, the outer diameter edge portion is elastically restored, whereby the seal fitting force can be improved.

前記芯材は非鉄金属からなるものとしても良い。この場合、外輪との間で線膨張係数差が発生する。軸受の高速回転により軸受の自己昇温が高まった場合、外輪シール溝よりも芯材の熱膨張量が大きくなり、シール嵌合力を向上させることができる。
前記芯材は、熱硬化性樹脂または熱可塑性樹脂からなるものとしても良い。これらの場合にも、軸受の自己昇温が高まった場合、外輪シール溝よりも芯材の熱膨張量が大きくなり、シール嵌合力を向上させ得る。 The core material may be made of a non-ferrous metal. In this case, a linear expansion coefficient difference occurs with the outer ring. When the self-heating temperature of the bearing increases due to the high-speed rotation of the bearing, the thermal expansion amount of the core material becomes larger than the outer ring seal groove, and the seal fitting force can be improved.
The core material may be made of a thermosetting resin or a thermoplastic resin. Also in these cases, when the self-temperature increase of the bearing is increased, the thermal expansion amount of the core material becomes larger than that of the outer ring seal groove, and the seal fitting force can be improved.

前記弾性部材の材質を、ニトリルゴム、アクリルゴム、フッ素ゴム、およびシリコンゴムの少なくともいずれか１つとしても良い。
前記シールは、芯材にゴム材を加硫成型して形成されたものであっても良い。 The material of the elastic member may be at least one of nitrile rubber, acrylic rubber, fluororubber, and silicon rubber.
The seal may be formed by vulcanizing and molding a rubber material on the core material.

この発明の転がり軸受は、内外輪間の軸受空間を密封するシールを有し、このシールの外径側の基端部が外輪シール溝に嵌合され外輪回転で用いられる転がり軸受において、前記シールは、環状の芯材とこの芯材を覆う弾性部材とを有し、前記芯材は、少なくとも前記基端部が弾性的に縮径可能な部位であり、前記シールは、前記基端部を前記外輪シール溝に嵌合するとき、前記基端部を半径方向内方に弾性変形させても、前記基端部が前記外輪シール溝に嵌合した状態で弾性復帰する前記基端部を備え、前記芯材の外径部は、前記外輪シール溝の入口径よりも小さく、前記芯材の外径部に、この芯材の外径縁部分が残るように円周方向に沿って複数の孔または切欠きを備え、前記複数の孔または切欠きを備えることにより、前記芯材の前記外径縁部分を弾性的に縮径可能とした。このため、外輪回転で用いられる転がり軸受において、組立性の向上を図ると共に、シール嵌合力の向上を図り、グリース漏れを抑制することができる。 The rolling bearing according to the present invention has a seal that seals a bearing space between the inner and outer rings, and the base end portion on the outer diameter side of the seal is fitted in the outer ring seal groove, and the seal is used in the rotation of the outer ring. Has an annular core material and an elastic member covering the core material, wherein the core material is a portion where at least the base end portion can be elastically reduced in diameter , and the seal includes the base end portion. wherein when fitted to the outer ring seal groove, even if the elastic deforming said proximal end portion radially inwardly, you elastic return in a state where the base end portion is fitted in the outer ring seal groove said proximal portion The outer diameter portion of the core material is smaller than the inlet diameter of the outer ring seal groove, and the outer diameter edge portion of the core material remains in the outer diameter portion of the core material along the circumferential direction. By providing a plurality of holes or notches, and by providing the plurality of holes or notches, The diameter edge portion and a resiliently contracted. For this reason, in the rolling bearing used in the outer ring rotation, it is possible to improve the assemblability, improve the seal fitting force, and suppress grease leakage.

この発明の第１の実施形態に係る転がり軸受の断面図である。It is sectional drawing of the rolling bearing which concerns on 1st Embodiment of this invention. 同転がり軸受のシール付近の断面図である。It is sectional drawing of the seal vicinity of the rolling bearing. 同シールにおける外径側の基端部を拡大して示す断面図である。It is sectional drawing which expands and shows the base end part by the side of the outer diameter in the seal | sticker. （Ａ）は同シールの芯材の斜視図、（Ｂ）は同芯材の正面図である。(A) is a perspective view of the core material of the seal, and (B) is a front view of the core material. （Ａ）は、同転がり軸受のシール挿入時におけるシール付近の断面図、（Ｂ）は、同転がり軸受のシール挿入後のシール付近の断面図である。(A) is sectional drawing of the seal vicinity at the time of seal insertion of the rolling bearing, (B) is sectional drawing of the seal vicinity after the seal insertion of the rolling bearing. 同シールのシールリップ部を拡大して示す断面図である。It is sectional drawing which expands and shows the seal lip part of the seal. （Ａ）は、この発明の他の実施形態に係る転がり軸受におけるシールの芯材の斜視図、（Ｂ）は同芯材の正面図である。(A) is a perspective view of the core material of the seal | sticker in the rolling bearing which concerns on other embodiment of this invention, (B) is a front view of a concentric material. （Ａ）は、この発明のさらに他の実施形態に係る転がり軸受におけるシールの芯材の斜視図、（Ｂ）は同芯材の正面図である。(A) is a perspective view of the core material of the seal in the rolling bearing which concerns on other embodiment of this invention, (B) is a front view of a concentric material. 参考提案例に係る転がり軸受におけるシールの芯材の正面図である。It is a front view of the core material of the seal | sticker in the rolling bearing which concerns on a reference proposal example . （Ａ）は、他の参考提案例に係る転がり軸受におけるシールの芯材の斜視図、（Ｂ）は同芯材の正面図である。(A) is a perspective view of the core material of the seal | sticker in the rolling bearing which concerns on another reference proposal example , (B) is a front view of a concentric material. （Ａ）は、従来例の転がり軸受の要部の断面図、（Ｂ）は、同転がり軸受におけるシールと外輪の間に隙間が発生した状態を示す断面図、（Ｃ）は、同転がり軸受からグリース漏れが発生した状態を示す断面図である。(A) is sectional drawing of the principal part of the rolling bearing of a prior art example, (B) is sectional drawing which shows the state which the clearance gap produced between the seal | sticker and outer ring in the rolling bearing, (C) is the rolling bearing. It is sectional drawing which shows the state which grease leaked from. （Ａ）は、従来例の転がり軸受につきシール嵌合力を向上させた例を示す断面図、（Ｂ）は同転がり軸受の要部の拡大断面図である。(A) is sectional drawing which shows the example which improved the seal fitting force about the rolling bearing of the prior art example, (B) is an expanded sectional view of the principal part of the rolling bearing.

この発明の第１の実施形態を図１ないし図６と共に説明する。
図１に示すように、この転がり軸受は、内外輪１，２の軌道面１ａ，２ａの間に複数の転動体３を介在させ、これら転動体３を保持する保持器４を設け、内外輪１，２間に形成される環状の軸受空間の両端をそれぞれシール５で密封している。この軸受内にはグリースが初期封入される。この転がり軸受は、転動体３を玉とした深溝玉軸受であり、内輪１を固定輪とし、外輪２を回転輪とした外輪回転で用いられる。ただしシール付き軸受としてアンギュラ玉軸受を適用することも可能である。 A first embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, in this rolling bearing, a plurality of rolling elements 3 are interposed between raceway surfaces 1a and 2a of inner and outer rings 1 and 2, and a cage 4 for holding these rolling elements 3 is provided. Both ends of an annular bearing space formed between 1 and 2 are sealed with seals 5 respectively. Grease is initially sealed in the bearing. This rolling bearing is a deep groove ball bearing in which the rolling elements 3 are balls, and is used for outer ring rotation in which the inner ring 1 is a fixed ring and the outer ring 2 is a rotating ring. However, an angular ball bearing can also be applied as a bearing with a seal.

図２に示すように、外輪２の内周面には、環状のシール５を圧入状態に嵌合固定する外輪シール溝２ｂが形成されている。シール５は、環状の芯材６と、この芯材６に一体に固着される弾性部材７とを有する。芯材６および弾性部材７の大部分により、シール本体８が構成される。このシール本体８は、径方向の中間部分１０およびこの中間部分１０に繋がる基端部１１を含む。   As shown in FIG. 2, an outer ring seal groove 2 b is formed on the inner peripheral surface of the outer ring 2 to fit and fix the annular seal 5 in a press-fitted state. The seal 5 includes an annular core member 6 and an elastic member 7 that is integrally fixed to the core member 6. A seal body 8 is constituted by most of the core member 6 and the elastic member 7. The seal body 8 includes a radial intermediate portion 10 and a proximal end portion 11 connected to the intermediate portion 10.

シール本体８の先端に、シールリップ部９が設けられる。このシールリップ部９を、内輪１に対して、アキシアル方向に接触する形状としている。また、この例では、弾性部材７は、芯材６の第２の立板部６ｃの内側面を除き芯材６の全体を覆うように設けられる。芯材６は、この例では、例えば、薄板状の鋼板などの金属材料から成る。シール５は、例えば、ゴム材を加硫成形して形成され、この加硫成形時に芯材６が弾性部材７に接着される。弾性部材７の材質として、例えば、ニトリルゴム、アクリルゴム、フッ素ゴム、およびシリコンゴムの少なくともいずれか１つが適用される。なお、図２のシール５は、外輪シール溝２ｂに挿入する前の自然状態を示している。シール５を外輪シール溝２ｂに挿入後、シールリップ部９の突起部分１６の一部が内輪シール溝１ｂにアキシアル接触する。   A seal lip portion 9 is provided at the tip of the seal body 8. The seal lip portion 9 is shaped to contact the inner ring 1 in the axial direction. In this example, the elastic member 7 is provided so as to cover the entire core material 6 except for the inner surface of the second upright plate portion 6 c of the core material 6. In this example, the core material 6 is made of a metal material such as a thin steel plate. The seal 5 is formed, for example, by vulcanization molding of a rubber material, and the core material 6 is bonded to the elastic member 7 during the vulcanization molding. As a material of the elastic member 7, for example, at least one of nitrile rubber, acrylic rubber, fluororubber, and silicon rubber is applied. 2 shows a natural state before being inserted into the outer ring seal groove 2b. After the seal 5 is inserted into the outer ring seal groove 2b, a part of the protruding portion 16 of the seal lip portion 9 is in axial contact with the inner ring seal groove 1b.

シール本体８の基端部１１は、中間部分１０に続く基端部分１２と、この基端部分１２から径方向外方へ延び外輪シール溝２ｂに嵌まり込む嵌込部分１３とを有する。
基端部１１のうち基端部分１２は、嵌込部分側に至るに従って先細り形状となる断面形状を有する。図３に示すように、基端部分１２は、軸受空間に対する外側の面が嵌込部分側に至るに従って軸受内側に傾斜する断面形状を有する。嵌込部分１３は、基端部分１２における最小の厚さと略同一肉厚でこの基端部分１２の基端から径方向外方へ延びる。 The base end portion 11 of the seal body 8 has a base end portion 12 that follows the intermediate portion 10 and a fitting portion 13 that extends radially outward from the base end portion 12 and fits into the outer ring seal groove 2b.
The base end portion 12 of the base end portion 11 has a cross-sectional shape that tapers as it reaches the fitting portion side. As shown in FIG. 3, the base end portion 12 has a cross-sectional shape that inclines toward the bearing inner side as the outer surface with respect to the bearing space reaches the fitting portion side. The fitting portion 13 has a thickness substantially the same as the minimum thickness of the base end portion 12 and extends radially outward from the base end of the base end portion 12.

図２に示すように、芯材６は、第１の立板部６ａと、円筒部６ｂと、第２の立板部６ｃと、傾斜部６ｄとを有する。第１の立板部６ａの内径側の基端に、円筒部６ｂを介して、第２の立板部６ｃが繋がっている。第１の立板部６ａは、第２の立板部６ｃよりも軸方向内側に配置され、これら第１，第２の立板部６ａ，６ｃは、それぞれ内外輪１，２の端面よりも軸方向内側で同端面に対し略平行に配置される。第２の立板部６ｃの先端には、内径側に向かうに従って軸方向内側に傾斜する傾斜部６ｄが繋がっている。   As shown in FIG. 2, the core member 6 includes a first upright plate portion 6a, a cylindrical portion 6b, a second upright plate portion 6c, and an inclined portion 6d. The second upright plate portion 6c is connected to the proximal end on the inner diameter side of the first upright plate portion 6a through the cylindrical portion 6b. The first upright plate portion 6a is disposed on the inner side in the axial direction than the second upright plate portion 6c, and the first and second upright plate portions 6a, 6c are respectively located on the end surfaces of the inner and outer rings 1, 2. It is arranged substantially parallel to the end face on the inner side in the axial direction. An inclined portion 6d that is inclined inward in the axial direction toward the inner diameter side is connected to the tip of the second standing plate portion 6c.

基端部１１の嵌込部分１３に、第１の立板部６ａの先端部分が埋め込まれ、基端部１１の基端部分１２に、第１の立板部６ａおよび円筒部６ｂが埋め込まれている。中間部分１０に、第２の立板部６ｃおよび傾斜部６ｄが埋め込まれている。この例では、シールリップ部９には、芯材６の各部が埋め込まれない構成になっている。   The distal end portion of the first standing plate portion 6 a is embedded in the fitting portion 13 of the proximal end portion 11, and the first standing plate portion 6 a and the cylindrical portion 6 b are embedded in the proximal end portion 12 of the proximal end portion 11. ing. A second standing plate portion 6c and an inclined portion 6d are embedded in the intermediate portion 10. In this example, each part of the core material 6 is not embedded in the seal lip part 9.

図４（Ａ）は、シール５の芯材６の斜視図であり、同図（Ｂ）は芯材６の正面図である。なお図４（Ａ），（Ｂ）は、芯材６における第１の立板部６ａおよび円筒部６ｂだけを示し、芯材６の他の部分については省略している。後述する図７〜図１０についても同じ。
図４（Ａ）に示すように、第１の立板部６ａの外径側の先端部分に、複数（この例では３箇所）の打ち抜き加工が施されている。図４（Ｂ）に示すように、第１の立板部６ａにおいて、打ち抜き加工された各孔１７は、それぞれ円周方向に定められた角度α１延び円周等配に設けられる。 FIG. 4A is a perspective view of the core material 6 of the seal 5, and FIG. 4B is a front view of the core material 6. 4A and 4B show only the first upright plate portion 6a and the cylindrical portion 6b in the core material 6, and other portions of the core material 6 are omitted. The same applies to FIGS. 7 to 10 described later.
As shown in FIG. 4A, a plurality of (three in this example) punching processes are performed on the outer diameter side tip portion of the first upright plate portion 6a. As shown in FIG. 4 (B), in the first upright plate portion 6a, the punched holes 17 are provided at an equally spaced circumference extending at an angle α1 determined in the circumferential direction.

第１の立板部６ａの外径部に、芯材６の外径縁部分６ａａが残るように円周方向に沿って前記複数の孔１７を設けることにより、芯材６の外径縁部分６ａａを弾性的に縮径可能としている。各外径縁部分６ａａは、この第１の立板部６ａの厚みよりも径方向肉厚ｔ１が薄い円弧状に形成される。孔１７により、第１の立板部６ａの外径縁部分６ａａが半径方向内方に弾性変形することを許容されると共に、第１の立板部６ａの外径縁部分６ａａは半径方向外方に弾性復帰し得る。   By providing the plurality of holes 17 along the circumferential direction so that the outer diameter edge portion 6aa of the core material 6 remains in the outer diameter portion of the first standing plate portion 6a, the outer diameter edge portion of the core material 6 6aa can be elastically reduced in diameter. Each outer diameter edge portion 6aa is formed in an arc shape whose radial thickness t1 is thinner than the thickness of the first standing plate portion 6a. The hole 17 allows the outer diameter edge portion 6aa of the first standing plate portion 6a to elastically deform radially inward, and the outer diameter edge portion 6aa of the first standing plate portion 6a is radially outward. Can be elastically restored.

図５（Ａ）は、転がり軸受のシール挿入時におけるシール付近の断面図であり、同図５（Ｂ）は、この転がり軸受のシール挿入後のシール付近の断面図である。図５（Ａ）に示すように、シール５の外径側の基端部１１を外輪シール溝２ｂに嵌合するとき、基端部１１を半径方向内方Ａ２に弾性変形させて縮径させる。このとき、打ち抜き加工された各貫通孔１７により、第１の立板部６ａの外径縁部分６ａａが半径方向内方Ａ２に弾性変形することを許容される。このように、外輪シール溝２ｂへのシール挿入時のシール５の弾性変形を容易に行える。
図５（Ｂ）に示すように、シール５の基端部１１が外輪シール溝２ｂに嵌合した状態で、シール５の基端部１１が弾性復帰する。これにより、従来技術のものよりシール嵌合力の向上を図っている。 FIG. 5A is a cross-sectional view of the vicinity of the seal when the seal of the rolling bearing is inserted, and FIG. 5B is a cross-sectional view of the vicinity of the seal after the seal of the rolling bearing is inserted. As shown in FIG. 5A, when the base end portion 11 on the outer diameter side of the seal 5 is fitted into the outer ring seal groove 2b, the base end portion 11 is elastically deformed radially inward A2 to reduce the diameter. . At this time, the punched through holes 17 allow the outer diameter edge portion 6aa of the first upright plate portion 6a to be elastically deformed radially inward A2. Thus, the elastic deformation of the seal 5 can be easily performed when the seal is inserted into the outer ring seal groove 2b.
As shown in FIG. 5B, the base end portion 11 of the seal 5 is elastically restored in a state where the base end portion 11 of the seal 5 is fitted in the outer ring seal groove 2b. As a result, the seal fitting force is improved as compared with the prior art.

図６に示すように、シールリップ部９は、外径側から順次、リップ本体部９ａと突起部分１６とを有する。リップ本体部９ａは、外径側から順次、リップ基端部１４と、くびれ部１５とを含む。これらリップ基端部１４、くびれ部１５、突起部分１６は一体に形成されている。リップ基端部１４は、芯材６の傾斜部６ｄの内周縁よりも内径側に所定距離延び、このシールリップ部９における径方向の基端部分となる。またリップ基端部１４における、軸受空間側の内側面および逆側の外側面は、それぞれ内径側先端に向かうに従って軸方向内側に至るように傾斜する断面形状に形成されている。   As shown in FIG. 6, the seal lip portion 9 has a lip body portion 9 a and a protruding portion 16 sequentially from the outer diameter side. The lip main body portion 9a includes a lip base end portion 14 and a constricted portion 15 sequentially from the outer diameter side. The lip base end portion 14, the constricted portion 15, and the protruding portion 16 are integrally formed. The lip base end portion 14 extends a predetermined distance from the inner peripheral edge of the inclined portion 6 d of the core member 6 toward the inner diameter side, and serves as a base end portion in the radial direction of the seal lip portion 9. In addition, the inner surface on the bearing space side and the outer surface on the opposite side of the lip base end portion 14 are each formed in a cross-sectional shape that is inclined so as to reach the inner side in the axial direction toward the distal end on the inner diameter side.

くびれ部１５は、シールリップ部９における径方向の中間部分となり、リップ基端部１４と突起部分１６との間に位置する。このくびれ部１５は、リップ基端部１４、突起部分１６よりも薄肉で且つ径方向に定められた距離延びる。シール本体８の基端部１１（図３）を外輪シール溝に嵌合させた状態で、突起部分１６の一部が内輪シール溝１ｂの一側面１ｂａにアキシアル接触すると共に、突起部分１６の他の一部がシール肩部１ｃに対しラビリンス隙間δ２を形成する。   The constricted portion 15 is an intermediate portion in the radial direction of the seal lip portion 9 and is located between the lip base end portion 14 and the protruding portion 16. The constricted portion 15 is thinner than the lip base end portion 14 and the protruding portion 16 and extends a distance determined in the radial direction. In a state where the base end portion 11 (FIG. 3) of the seal body 8 is fitted in the outer ring seal groove, a part of the projecting portion 16 is in axial contact with one side surface 1ba of the inner ring seal groove 1b. Forms a labyrinth gap δ2 with respect to the seal shoulder 1c.

作用効果について説明する。
シール５の外径側の基端部１１を外輪シール溝２ｂに嵌合するとき、基端部１１を半径方向内方に弾性変形させて縮径させる。このシール５の基端部１１が外輪シール溝２ｂに嵌合した状態で、シール５の基端部１１が弾性復帰する。芯材６を少なくとも基端部１１が弾性的に縮径可能な形状および材質を持つようにしたため、シール５の基端部１１を外輪シール溝２ｂに挿入するとき、シール５の基端部１１が弾性変形したまま外輪シール溝２ｂに嵌り込み易くなり、転がり軸受の組立性の向上を図ることができる。またシール５の基端部１１が外輪シール溝２ｂに嵌合した状態で基端部１１が弾性復帰するため、シール嵌合力の向上を図り、外輪シール溝２ｂ内で外輪２とシール５とが隙間なく密着し、軸受からのグリース漏れを抑制することができる。
芯材６の外径部に、この芯材６の外径縁部分６ａａが残るように円周方向に沿って複数の孔１７を設けることにより、芯材６の外径縁部分６ａａを弾性的に縮径可能としている。この場合、一般的に用いられる金属製の芯材に打ち抜き加工を施すことで、前記外径縁部分６ａａを簡単に設けることができる。この場合、芯材を切削加工等するものより製造コストの低減を図れる。 The effect will be described.
When the base end portion 11 on the outer diameter side of the seal 5 is fitted into the outer ring seal groove 2b, the base end portion 11 is elastically deformed radially inward to reduce the diameter. With the base end portion 11 of the seal 5 fitted in the outer ring seal groove 2b, the base end portion 11 of the seal 5 is elastically restored. Since at least the base end portion 11 of the core material 6 has a shape and material that can be elastically reduced in diameter, the base end portion 11 of the seal 5 is inserted when the base end portion 11 of the seal 5 is inserted into the outer ring seal groove 2b. Can be easily fitted into the outer ring seal groove 2b while being elastically deformed, and the assemblability of the rolling bearing can be improved. Further, since the base end portion 11 is elastically restored in a state where the base end portion 11 of the seal 5 is fitted in the outer ring seal groove 2b, the seal fitting force is improved, and the outer ring 2 and the seal 5 are connected in the outer ring seal groove 2b. It adheres without a gap and can suppress grease leakage from the bearing.
The outer diameter edge portion 6aa of the core material 6 is made elastic by providing a plurality of holes 17 along the circumferential direction so that the outer diameter edge portion 6aa of the core material 6 remains in the outer diameter portion of the core material 6. The diameter can be reduced. In this case, the outer diameter edge portion 6aa can be easily provided by punching a commonly used metal core. In this case, it is possible to reduce the manufacturing cost compared to cutting the core material.

他の実施形態について説明する。
以下の説明においては、先行する形態で説明している事項に対応している部分には同一の参照符を付し、重複する説明を略する。構成の一部のみを説明している場合、構成の他の部分は、先行して説明している形態と同様とする。実施の各形態で具体的に説明している部分の組合せばかりではなく、特に組合せに支障が生じなければ、実施の形態同士を部分的に組合せることも可能である。 Another embodiment will be described.
In the following description, the same reference numerals are given to the portions corresponding to the matters described in the preceding embodiment, and the overlapping description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

図７（Ａ），（Ｂ）に示すように、芯材６の第１の立板部６ａの外径部に、この芯材６の外径縁からなる片持ち状片６ａｂ，６ａｂを形成する切欠きＳＬを形成することにより、芯材６の外径縁部分を弾性的に縮径可能としても良い。この場合、例えば、前記と同様に、第１の立板部６ａに打ち抜き加工を施して複数の孔１７を設けたうえで、芯材６の外径縁からなる片持ち状片６ａｂ，６ａｂを形成する切欠きＳＬを形成している。このように片持ち状片６ａｂ，６ａｂを設けることで、シール嵌合力を微調整することが可能となる。   As shown in FIGS. 7A and 7B, cantilevered pieces 6ab and 6ab made of the outer diameter edge of the core member 6 are formed on the outer diameter portion of the first standing plate portion 6a of the core member 6. By forming the notch SL to be formed, the outer diameter edge portion of the core material 6 may be elastically reduced in diameter. In this case, for example, in the same manner as described above, the first upright plate portion 6a is punched to provide a plurality of holes 17, and the cantilevered pieces 6ab and 6ab formed of the outer diameter edge of the core material 6 are attached. A notch SL to be formed is formed. Thus, by providing the cantilevered pieces 6ab, 6ab, the seal fitting force can be finely adjusted.

図８（Ａ），（Ｂ）に示すように、芯材６において、芯材全体における円周方向の一部が半径方向に切欠かれた切欠きＳＬ１を設けても良い。このように芯材６の一部に切欠きＳＬ１を設けて弾性復元性部材とすると、廃棄する材料の低減を図れ、シール嵌合力の向上を簡単に図れる。したがって、転がり軸受の組立性の向上を図ることができると共に、シール嵌合力の向上を図って軸受からのグリース漏れを抑制することができる。   As shown in FIGS. 8A and 8B, the core material 6 may be provided with a notch SL1 in which a part of the entire core material in the circumferential direction is notched in the radial direction. Thus, when the notch SL1 is provided in a part of the core material 6 to provide an elastic restoring member, the material to be discarded can be reduced, and the seal fitting force can be easily improved. Therefore, it is possible to improve the assemblability of the rolling bearing and to improve the seal fitting force and suppress the grease leakage from the bearing.

参考提案例として、図９に示すように、芯材６の外径縁部分６ａａを、芯材６の外径部の残余の部分よりも拡径させても良い。各外径縁部分６ａａは、半径方向中間部が最も半径方向外方に突出する。この場合、シールの基端部を外輪シール溝に嵌合するとき、外径縁部分６ａａが半径方向内方に弾性変形することで、シールを外輪シール溝に容易に挿入し得る。シールの基端部が外輪シール溝に嵌合した状態で、外径縁部分６ａａが弾性復帰することで、シールの嵌合力の向上を図れる。したがって組立性の向上を図ると共に、シール嵌合力の向上を図り、グリース漏れを抑制し得る。 As an example of reference proposal, as shown in FIG. 9, the outer diameter edge portion 6aa of the core material 6 may be expanded in diameter compared to the remaining portion of the outer diameter portion of the core material 6. As for each outer-diameter edge part 6aa, a radial direction intermediate part protrudes most radially outward. In this case, when the base end portion of the seal is fitted into the outer ring seal groove, the outer diameter edge portion 6aa is elastically deformed radially inward, so that the seal can be easily inserted into the outer ring seal groove. In the state where the base end portion of the seal is fitted in the outer ring seal groove, the outer diameter edge portion 6aa is elastically restored, whereby the fitting force of the seal can be improved. Therefore, it is possible to improve the assemblability, improve the seal fitting force, and suppress grease leakage.

他の参考提案例として、図１０（Ａ），（Ｂ）に示すように、各外径縁部分６ａａの円周方向の一部に切欠きＳＬ２を設けても良い。この場合、シールの基端部を外輪シール溝に嵌合するとき、各外径縁部分６ａａにおける、切欠きＳＬ２を設けた先端部が半径方向内方に弾性変形することで、シールを外輪シール溝に容易に挿入し得る。シールの基端部が外輪シール溝に嵌合した状態で、各外径縁部分６ａａの先端部が弾性復帰することで、シールの嵌合力の向上を図れる。したがって組立性の向上を図ると共に、シール嵌合力の向上を図り、グリース漏れを抑制し得る。 As another reference proposal example, as shown in FIGS. 10A and 10B, a notch SL <b> 2 may be provided in a part in the circumferential direction of each outer diameter edge portion 6aa. In this case, when the base end portion of the seal is fitted into the outer ring seal groove, the distal end portion provided with the notch SL2 in each outer diameter edge portion 6aa is elastically deformed radially inward, so that the seal is sealed with the outer ring seal. Can be easily inserted into the groove. In the state where the base end portion of the seal is fitted in the outer ring seal groove, the distal end portion of each outer diameter edge portion 6aa is elastically restored, whereby the fitting force of the seal can be improved. Therefore, it is possible to improve the assemblability, improve the seal fitting force, and suppress grease leakage.

芯材は非鉄金属からなるものとしても良い。この場合、外輪との間で線膨張係数差が発生する。軸受の高速回転により軸受の自己昇温が高まった場合、外輪シール溝よりも芯材の熱膨張量が大きくなり、シール嵌合力を向上させることができる。
芯材は、熱硬化性樹脂または熱可塑性樹脂からなるものとしても良い。これらの場合にも、軸受の自己昇温が高まった場合、外輪シール溝よりも芯材の熱膨張量が大きくなり、シール嵌合力を向上させ得る。 The core material may be made of a non-ferrous metal. In this case, a linear expansion coefficient difference occurs with the outer ring. When the self-heating temperature of the bearing increases due to the high-speed rotation of the bearing, the thermal expansion amount of the core material becomes larger than the outer ring seal groove, and the seal fitting force can be improved.
The core material may be made of a thermosetting resin or a thermoplastic resin. Also in these cases, when the self-temperature increase of the bearing is increased, the thermal expansion amount of the core material becomes larger than that of the outer ring seal groove, and the seal fitting force can be improved.

シールは、初期は接触タイプであったシールが、運転後、摩耗により非接触または軽接触タイプのシールとなるものとしても良い。この場合、軸受の運転により、シールリップ部の突起部分を有効に摩耗させ、トルク低減を図ると共に耐異物侵入性の向上を図ることができる。
シールは、芯材の一部にゴム材を加硫成型して形成されたものであっても良い。
シールリップ部を、内輪に対してラジアル方向に接触する形状としても良い。この場合において、内輪は、内輪外周面にシール溝のない形態としても良い。 The seal may be a non-contact type or a light contact type seal due to wear after operation. In this case, by operating the bearing, the protruding portion of the seal lip portion can be effectively worn to reduce the torque and improve the resistance to foreign matter penetration.
The seal may be formed by vulcanizing and molding a rubber material on a part of the core material.
It is good also as a shape which a seal lip part contacts in a radial direction with respect to an inner ring | wheel. In this case, the inner ring may have a form without a seal groove on the outer peripheral surface of the inner ring.

１…内輪
２…外輪
２ｂ…外輪シール溝
５…シール
６…芯材
６ａａ…外径縁部分
７…弾性部材
１１…基端部
１７…孔
ＳＬ，ＳＬ１，ＳＬ２…切欠き
DESCRIPTION OF SYMBOLS 1 ... Inner ring 2 ... Outer ring 2b ... Outer ring seal groove 5 ... Seal 6 ... Core material 6aa ... Outer diameter edge part 7 ... Elastic member 11 ... Base end part 17 ... Hole SL, SL1, SL2 ... Notch

Claims (2)

内外輪間の軸受空間を密封するシールを有し、このシールの外径側の基端部が外輪シール溝に嵌合され外輪回転で用いられる転がり軸受において、
前記シールは、環状の芯材とこの芯材を覆う弾性部材とを有し、
前記芯材は、少なくとも前記基端部が弾性的に縮径可能な部位であり、前記シールは、前記基端部を前記外輪シール溝に嵌合するとき、前記基端部を半径方向内方に弾性変形させても、前記基端部が前記外輪シール溝に嵌合した状態で弾性復帰する前記基端部を備え、前記芯材の外径部は、前記外輪シール溝の入口径よりも小さく、前記芯材の外径部に、この芯材の外径縁部分が残るように円周方向に沿って複数の孔または切欠きを備え、前記複数の孔または切欠きを備えることにより、前記芯材の前記外径縁部分を弾性的に縮径可能とした転がり軸受。 In a rolling bearing that has a seal that seals the bearing space between the inner and outer rings, and the base end portion on the outer diameter side of this seal is fitted in the outer ring seal groove, and used for outer ring rotation.
The seal has an annular core material and an elastic member that covers the core material,
The core material is a portion where at least the base end portion can be elastically reduced in diameter , and when the seal is fitted into the outer ring seal groove, the base end portion is radially inward. elastic be deformed, with said proximal end you elastic return in a state where the base end portion is fitted in the outer ring seal groove, the outer diameter of the core material, inlet diameter of the outer ring seal groove A plurality of holes or notches along the circumferential direction so that an outer diameter edge portion of the core material remains in the outer diameter portion of the core material, and the plurality of holes or notches are provided. Accordingly, the outer diameter edge portions resiliently reduced in diameter translocation rising bearing of the core material. 請求項１に記載の転がり軸受において、前記芯材は非鉄金属からなる転がり軸受。 The rolling bearing according to claim 1 , wherein the core material is made of a non-ferrous metal.
JP2013016340A 2013-01-31 2013-01-31 Rolling bearing Expired - Fee Related JP6104620B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2013016340A JP6104620B2 (en) 2013-01-31 2013-01-31 Rolling bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013016340A JP6104620B2 (en) 2013-01-31 2013-01-31 Rolling bearing

Publications (2)

Publication Number Publication Date
JP2014148992A JP2014148992A (en) 2014-08-21
JP6104620B2 true JP6104620B2 (en) 2017-03-29

Family

ID=51572139

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2013016340A Expired - Fee Related JP6104620B2 (en) 2013-01-31 2013-01-31 Rolling bearing

Country Status (1)

Country Link
JP (1) JP6104620B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111520399A (en) * 2020-04-20 2020-08-11 人本集团有限公司 Novel deep groove ball bearing

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4531447Y1 (en) * 1966-08-16 1970-12-03
JPH08247156A (en) * 1995-03-07 1996-09-24 Uchiyama Mfg Corp Bearing seal
JP3691183B2 (en) * 1996-11-27 2005-08-31 内山工業株式会社 Bearing seal
JP3607538B2 (en) * 1999-07-07 2005-01-05 内山工業株式会社 Bearing seal and manufacturing method thereof
JP2002174255A (en) * 2000-12-04 2002-06-21 Uchiyama Mfg Corp Bearing with bearing seal

Also Published As

Publication number Publication date
JP2014148992A (en) 2014-08-21

Similar Documents

Publication Publication Date Title
JP6686692B2 (en) Wheel bearing device
EP2639467B1 (en) Cartridge seal for a wheel hub rolling bearing unit
JP5969267B2 (en) Bearing for outer ring rotation
JP6214891B2 (en) Bearing device with sealing device
JP6104620B2 (en) Rolling bearing
WO2017204058A1 (en) Bearing sealing device
US20150330454A1 (en) Rolling bearing
US20110135231A1 (en) Seal and a Rolling Bearing including the Seal
JP3201303U (en) Sealing device
JP2009074589A (en) Sealing device
JP5293420B2 (en) Sealing device
WO2011142217A1 (en) Ball bearing with both sides sealed
JP2017125617A (en) Roller bearing
JP6649818B2 (en) Sealing member
JP3897013B2 (en) Water pump device
JP2008190663A (en) Ball bearing
KR101867405B1 (en) Wheel bearing
WO2024053511A1 (en) Wheel bearing device
JP5834551B2 (en) Manufacturing method of rolling bearing
JP2011202774A (en) Rolling bearing, seal, and seal attachment method
JP2010090986A (en) Sealed rolling bearing
JP2009299873A (en) Sealing device
JP2009287626A (en) Rolling bearing device
JP2012072813A (en) Bearing for rotating outer ring and pulley using the same
JP6565234B2 (en) Rolling bearing with sealing device and sealing device for rolling bearing

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20150918

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20160608

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20160712

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20160912

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20170214

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20170301

R150 Certificate of patent or registration of utility model

Ref document number: 6104620

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

LAPS Cancellation because of no payment of annual fees